CN202707496U - Variable-capacity rotary compressor - Google Patents
Variable-capacity rotary compressor Download PDFInfo
- Publication number
- CN202707496U CN202707496U CN 201220378264 CN201220378264U CN202707496U CN 202707496 U CN202707496 U CN 202707496U CN 201220378264 CN201220378264 CN 201220378264 CN 201220378264 U CN201220378264 U CN 201220378264U CN 202707496 U CN202707496 U CN 202707496U
- Authority
- CN
- China
- Prior art keywords
- groove
- cylinder
- flange
- rotary compressor
- sliding
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
Links
- 238000005096 rolling process Methods 0.000 claims description 26
- 238000005192 partition Methods 0.000 claims description 21
- 230000033001 locomotion Effects 0.000 abstract description 4
- 239000003921 oil Substances 0.000 description 9
- 238000007789 sealing Methods 0.000 description 9
- 239000007788 liquid Substances 0.000 description 6
- 230000008859 change Effects 0.000 description 5
- 238000004378 air conditioning Methods 0.000 description 3
- 230000003068 static effect Effects 0.000 description 3
- 230000009471 action Effects 0.000 description 2
- 230000007812 deficiency Effects 0.000 description 2
- 238000006073 displacement reaction Methods 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 238000003754 machining Methods 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 230000003584 silencer Effects 0.000 description 2
- 238000006243 chemical reaction Methods 0.000 description 1
- 238000004134 energy conservation Methods 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
- 230000007246 mechanism Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000005057 refrigeration Methods 0.000 description 1
Images
Landscapes
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
The utility model discloses a variable-capacity rotary compressor, which comprises a shell, a motor and a cylinder assembly, wherein the motor and the cylinder assembly are arranged in the shell; the motor is connected with the cylinder assembly through a crankshaft; an elastic component is arranged at the tail part of a first sliding blade; an elastic component is omitted at the tail part of a second sliding blade; a groove is arranged in the second sliding blade or at a position of a second flange, which corresponds to the second sliding blade, or at a position of an intermediate baffle plate, which corresponds to the second sliding blade; a passage for being communicated with the groove is arranged on the cylinder assembly; the variable-capacity rotary compressor also comprises a gas switching device; and the gas switching device switches a pressure at the groove between a high-pressure-side pressure and a low-pressure-side pressure. The motions of the sliding blades are controlled through a pressure difference; the switching between single-cylinder running and double-cylinder running can be reliably realized; the leakage is effectively prevented; when the sliding blades are immobile, high pressures are both inside a cylinder and at the tail part of a sliding blade groove; and the mixing of the high pressure and the low pressure is avoided.
Description
Technical Field
The utility model relates to a compressor field, especially a variable capacity rotary compressor.
Background
Energy conservation and environmental protection are development trends of the air conditioning industry, a common air conditioning system adopts a constant volume compressor, and the compressor can be repeatedly started and stopped if the room temperature reaches a set temperature during operation, so that on one hand, energy is consumed, on the other hand, room temperature change is caused, and the comfort is damaged, the compressor capacity control technology is a technology between frequency conversion and constant volume, the purpose of improving the performance of the compressor by changing the capacity of the compressor along with the change of the air conditioning load can be achieved, the variable frequency compressor can be combined to make up the deficiency of capacity adjustment of the variable frequency compressor, the conventional variable capacity rotary compressor is provided with two sliding sheets and two oil discharge holes on a single air cylinder respectively, the compressor is also provided with a pressure switching mechanism for switching the pressure of a second sliding sheet cavity between the high-pressure side pressure and the low-pressure side pressure, and the, and an operation mode that the first sliding sheet and the second sliding sheet work simultaneously so as to change the displacement of the cylinder, namely, the displacement of the cylinder is controlled by one cylinder. Such structure easily causes the air leakage, and when the gleitbretter was static, gas leakage phenomenon can appear in gleitbretter department moreover.
SUMMERY OF THE UTILITY MODEL
For overcoming the deficiencies of the prior art, the utility model provides a reasonable in design, simple structure's variable capacity rotary compressor, the utility model discloses the technical scheme who realizes that above-mentioned purpose adopts is:
a variable capacity rotary compressor comprises a shell, a motor and a cylinder assembly, wherein the motor and the cylinder assembly are arranged in the shell and connected through a crankshaft, the cylinder assembly comprises a first cylinder, a second cylinder, a first rolling rotor and a second rolling rotor which are respectively arranged in the first cylinder and the second cylinder and can eccentrically rotate, a first sliding sheet arranged in the first cylinder, a second sliding sheet arranged in the second cylinder, a middle partition plate, a first flange, a second flange and a gas switching device;
a groove is formed in the second sliding sheet or in the position, corresponding to the second sliding sheet, of the second flange or in the position, corresponding to the second sliding sheet, of the middle partition plate;
a gas channel is arranged between the groove and the gas switching device;
the gas switching device is used for switching the gas pressure at the groove between a high pressure and a low pressure, when the gas pressure at the groove is the high pressure, the second sliding sheet is in a working state, and when the gas pressure at the groove is the low pressure, the second sliding sheet is in a locking state.
Preferably, the groove is arranged on the second sliding sheet and is positioned on the surface contacting with the second flange, and the gas channel is positioned on the second flange;
the distance from the inner wall of the groove to the outer wall of the second sliding sheet is greater than or equal to 0.5 mm-1.2 mm, and the diameter of the gas channel is smaller than or equal to the width of the groove.
Preferably, when the second rolling rotor is located at a top dead center, the center of the gas channel coincides with the center of the second slide vane, and the distance from the inner wall of the groove closest to the outer edge of the second flange is 2mm to 5 mm.
Preferably, the groove is formed in the second flange on a surface contacting the second sliding piece, and the gas passage is formed in the second flange.
Preferably, a bypass is further arranged on the side wall of the gas channel and is used for being communicated with the gas channel.
Preferably, the distance from the inner wall of the groove to the outer wall of the second sliding piece is greater than or equal to 0.5 mm-1.2 mm, and the diameter of the gas channel is smaller than or equal to the width of the groove.
Preferably, when the second rolling rotor runs to the bottom dead center, the sum of the shortest distance from the end point of the groove close to the inner wall of the second cylinder and the length of the groove minus the sum of the length of the sliding piece and the stroke of the sliding piece is less than or equal to 2 mm-5 mm.
Preferably, the groove is formed in the middle partition plate and located on a surface, which is in contact with the second sliding piece, of the middle partition plate, and the gas channel is located in the middle partition plate.
Preferably, the distance from the inner wall of the groove to the outer wall of the second sliding piece is greater than or equal to 0.5 mm-1.2 mm, and the diameter of the gas channel is less than or equal to the width of the groove;
when the second rolling rotor is positioned at the bottom dead center, the sum of the shortest distance from the end point of the groove close to the inner wall of the second cylinder and the length of the groove minus the sum of the length of the sliding piece and the stroke of the sliding piece is less than or equal to 2 mm-5 mm.
Preferably, the gas switching device is at least one of a three-way valve and a four-way valve.
The utility model has the advantages that: the sliding sheet, the flange or the middle partition plate is provided with a groove, the shape of the groove can be in various forms, a gas channel communicated with the groove is arranged on the finish machining end face of the flange or the middle partition plate, the channel is connected with a gas switching device, and the gas switching device is controlled through electromagnetic machinery to change the pressure in the groove into high pressure or low pressure, so that the working or locking of the sliding sheet is controlled, and the purpose of capacity control is achieved; the sliding sheet is pressed by the pressure generated by the pressure difference, so that the switching of the single-cylinder and double-cylinder operation can be reliably realized, and the stability and the reliability of the operation are higher; meanwhile, leakage can be well prevented by the regulation of the sealing size; when the sliding vane is static, the interior of the air cylinder and the tail part of the groove of the sliding vane are both high-pressure, so that air leakage of high pressure and low pressure is avoided; the structure is simple and reasonable, the volume is small, and the manufacturing cost is low.
Drawings
Fig. 1 is a sectional view of a vane of an embodiment of a variable capacity rotary compressor according to the present invention, in which a groove is formed;
fig. 2 is a partial sectional view of the variable capacity rotary compressor shown in fig. 1;
FIG. 3 is a perspective view of a vane of the variable capacity rotary compressor shown in FIG. 1;
FIG. 4 is a top view of the slider shown in FIG. 3;
fig. 5 is a plan view of a lower flange of the capacity variable rotary compressor shown in fig. 1;
fig. 6 is a cross-sectional view of a groove formed on a lower flange of an embodiment of the variable capacity rotary compressor of the present invention;
fig. 7 is a partial sectional view of the variable capacity rotary compressor shown in fig. 6;
FIG. 8 is a top view of a vane of the variable capacity rotary compressor shown in FIG. 6;
fig. 9 is a plan view of a lower flange of the capacity variable rotary compressor shown in fig. 6;
fig. 10 is a schematic view illustrating the fitting of a lower cylinder and a lower flange of the variable capacity rotary compressor shown in fig. 6; wherein,
1, a compressor exhaust pipe; 2, an upper cover component; 3, a shell; 4, a stator component; 5 a rotor assembly;
6, a crankshaft; 7, an upper flange; 8, a silencer; 9 sliding the upper blade; 10 an upper cylinder; 11 a spring;
12 a middle partition plate; 13 lower cylinders; 14 lower sliding sheets; 15 lower flange; 16 mounting plates; 17 a lower cover;
18 a lower cover plate; 19 liquid separator; 20 an upper air suction pipe; 21, a lower air suction pipe; 22 an upper eccentric portion;
23 lower eccentric part; 24 oil guide sheets; 25 rolling the rotor; 26 lower rolling rotors;
27 gas switching means; 271 a first inlet; 272 a second inlet; 273 a first outlet;
274 a second outlet; 28 grooves; 29 lower flange channel; 30 flange side holes;
31 lower cylinder suction pipe.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention more clearly understood, the following description, with reference to the accompanying drawings and embodiments, is made for the following cylinder as an example of the dual-rotor rotary compressor of the second cylinder, and the present invention will be described in further detail with respect to the variable capacity rotary compressor and the control method thereof. It should be understood that the specific embodiments described herein are only for explaining the present invention, and are not intended to limit the lower cylinder of the variable capacity rotary compressor described in the present invention to the second cylinder.
Referring to fig. 1 to 5, the upper cylinder is a first cylinder, and the lower cylinder is a second cylinder, and the lower cylinder may be the first cylinder, and the upper cylinder may be the second cylinder:
the double-rotor rotary compressor comprises a compressor exhaust pipe 1, an upper cover component 2 and a shell 3; the stator assembly 4, the rotor assembly 5, the crankshaft 6, the upper flange 7, the upper silencer 8, the upper slide sheet 9, the upper cylinder 10, the spring 11, the middle partition plate 12, the lower cylinder 13, the lower slide sheet 14, the lower flange 15, the mounting plate 16, the lower cover 17, the lower cover plate 18, the liquid separator 19, the upper air suction pipe 20, the lower air suction pipe 21, the upper eccentric part 22, the lower eccentric part 23, the oil guide sheet 24, the upper rolling rotor 25, the lower rolling rotor 26, the gas switching device 27, the lower flange groove 28, the lower flange channel 29, the lower flange bypass hole 30 and the lower cylinder air suction pipe 31.
In the housing 3, a cylinder assembly of the compressor and a rotor assembly 5 of the motor are connected by a crankshaft 6, the crankshaft 6 has an upper eccentric portion 22 and a lower eccentric portion 23 formed integrally, the two eccentric portions have a phase difference of 180 degrees, an upper rolling rotor 25 is assembled on an outer circumferential surface of the upper eccentric portion 22, a lower rolling rotor 26 is assembled on an outer circumferential surface of the lower eccentric portion 23, and the upper rolling rotor 25 and the lower rolling rotor 26 respectively serve as rolling pistons.
The centrifugal oil pump is arranged at the lower end of the crankshaft 6 and is concentric with the crankshaft 6, the centrifugal oil pump comprises a thin-wall circular tube and a spiral oil guide sheet 24 inserted into the middle of the thin-wall circular tube, the crankshaft 6 drives the oil guide sheet 24 to rotate when rotating, liquid lubricating oil rises along the wall surface of the thin-wall circular tube under the action of centrifugal force, the oil can be pumped to a certain height, and the eccentric amount of the crankshaft is e.
Wherein the cylinder assembly comprises an upper cylinder 10, a lower cylinder 13, an upper rolling rotor 25 arranged in the upper cylinder 10, a lower rolling rotor 26 arranged in the lower cylinder 13, an upper sliding sheet 9 arranged on the upper cylinder 10 and a lower sliding sheet 14 arranged on the lower cylinder 13, the upper sliding sheet 9 and the lower sliding sheet 14 can contact with the rolling rotors and do linear reciprocating motion along the radial direction of the rolling rotors in respective sliding sheet grooves (not shown) so as to respectively divide the upper cylinder 10 and the lower cylinder 13 into a suction cavity and a discharge cavity, the tail part of the upper sliding sheet 9 is provided with a spring 11, the elastic force of the spring 11 acts on the upper sliding sheet 9, so that the upper sliding sheet 9 always contacts with the upper rolling rotor; the tail of the lower slide 14 is free of elastic members.
A middle partition plate 12 is arranged between the upper cylinder 10 and the lower cylinder 13, the middle partition plate 12 is used for sealing the lower end part of the upper cylinder 10 and the upper end part of the lower cylinder 13, the upper end part of the upper cylinder 10 is sealed by an upper flange 7, and the lower end part of the lower cylinder 13 is sealed by a lower flange 15;
the upper cylinder is provided with a first intake port (not shown) and a first exhaust port (not shown); the lower cylinder is provided with a second air inlet (namely a lower cylinder air suction pipe 31) and a second air outlet (not shown); the first and second exhaust ports communicate with the interior of the casing 3 and thus with the compressor discharge duct 1, the first intake port communicates with the upper intake duct 20, and the second intake port (lower cylinder intake duct 31) communicates with the lower intake duct 21;
the compressor is externally connected with a gas switching device 27 and a liquid distributor 19, an inlet of the liquid distributor 19 is connected with an indoor evaporator, two outlets of the liquid distributor 19 are respectively connected with an upper suction pipe 20 of an upper cylinder 10 and a first inlet 271 of the gas switching device 27, a second inlet 272 of the gas switching device 27 is connected with a compressor exhaust pipe 1, a first outlet 273 of the gas switching device 27 is connected with a lower suction pipe 21 of a lower cylinder 13, a second outlet 274 of the gas switching device 27 is used for communicating a gas channel arranged between the groove 28 and the gas switching device, and the gas switching device 27 is a four-way reversing valve.
The first embodiment is as follows:
as shown in fig. 1 to 5, a groove 28 is provided on an end surface of the lower sliding piece 14, the provision of the groove 28 is equivalent to opening a blind hole on the lower sliding piece 14, the shape of the groove 28 may be square or circular, preferably square, the end surface of the upper groove 28 on the lower sliding piece 14 is in contact with a sealing end surface of a lower flange 15, a lower flange passage 29 for communicating the groove 28 is provided on the lower flange 15, the diameter of the lower flange passage 29 is d, and the lower flange passage 29 may be provided as a through hole for communicating with a second outlet of the gas switching device 27; however, in order to facilitate the pipe connection, the lower end of the lower flange channel 29 is not opened and becomes a blind hole, a lower flange bypass hole 30 is arranged on the side wall of the lower flange channel 29, and the lower flange bypass hole 30 is communicated with the lower flange channel 29 and is used for communicating with a second outlet of the gas switching device 27; of course, as an alternative embodiment, the lower flange passage 29 and the lower flange bypass hole 30 may be formed in the middle partition 12.
In order to ensure sealing, the distance from the inner wall of the groove 28 to the outer wall of the lower slide 14 is greater than or equal to 0.5-1.2 mm, and the diameter d of the lower flange channel 29 is less than or equal to the width A of the groove 28. Preferably, the groove 28 is located on the center line of the lower sliding piece 14 in the width direction, when the center line of the groove 28 is coincident with the center line of the lower sliding piece 14 in the width direction, B-A is larger than or equal to 2 x (0.5-1.2) mm, and d is smaller than or equal to A; where B is the width of the lower sliding piece 14, the value of B-a is not required to be large because of the pressure difference, as long as a certain sealing distance is sufficient, and preferably, the single-side sealing distance of the groove 28 is between 0.5 and 1.2mm, i.e. B-a =2 × (0.5 and 1.2) mm.
When the lower rolling rotor 26 is positioned at the top dead center, the center of the lower flange channel 29 is overlapped with the center of the lower sliding vane 14, the distance from the inner wall, closest to the outer edge of the lower flange 15, of the groove 28 to the outer edge of the lower flange 15 is 2-5 mm, namely the distance from the tail part P of the groove 28 to the excircle of the lower flange 15 is 2-5 mm;
when the first inlet 271 and the first outlet 273 of the four-way valve are communicated and the second inlet 272 and the second outlet 274 of the four-way valve are communicated, the two-cylinder mode motion is performed;
when the first inlet 271 and the second outlet 274 of the four-way valve are communicated, and the second inlet 272 and the first outlet 273 of the four-way valve are communicated, single-cylinder mode motion is performed;
under normal conditions, the compressor operates in two cylinders, at this time, the suction pipe 31 of the lower cylinder is at low pressure, the bypass hole 30 of the lower flange is at high pressure, and the groove 28 of the lower sliding vane 14 is at high pressure and is equivalent to the pressure in the shell 3, so that no pressure difference is formed between the gas in the groove 28 and the gas in the shell 3, and at this time, no pressure difference exists between the contact end surface of the groove 28 of the lower sliding vane 14 and the lower flange, that is, no friction exists, the lower sliding vane 14 normally reciprocates, the lower cylinder 13 normally operates, and the compressor operates in two cylinders.
When the lower cylinder intake pipe 31 is switched to high pressure, the lower flange bypass hole 30 is switched to low pressure, and the groove 28 is also switched to low pressure. At this time, the pressure around the lower sliding piece 14 is the pressure of the gas inside the casing 3 and has a pressure difference with the lower flange groove 28, so that the lower end surface of the lower sliding piece 14 and the upper end surface of the lower flange generate friction force. Therefore, the inside of the lower cylinder 13 is high-pressure gas and the pressure of the gas in the shell 3 is equivalent, so that the head and the tail of the sliding sheet have no pressure difference, and the problem of leakage does not exist.
When the lower sliding vane 14 moves to a certain position (top dead center), the sliding vane stops reciprocating under the action of friction force, and accordingly the sliding vane stops in the lower sliding vane groove, the lower cylinder 13 is unloaded, and the compressor operates in a single cylinder.
At this time, the groove 28 is used for expanding the stressed area of the lower sliding vane 14 and enabling the lower end surface of the lower sliding vane 14 to be in contact with the upper end surface of the lower flange 15, so that the leakage amount of gas or refrigeration oil is reduced when the single-cylinder operation is carried out, and the stability of the performance of the compressor is ensured.
Example two:
referring to fig. 6 to 10, as another embodiment, the difference from embodiment 1 is that a groove 28 is provided on the lower flange 15 on one end surface of the lower flange 15 that is engaged with the lower cylinder 13, preferably, a center line of the groove 28 faces a center line of the lower vane 14, a lower flange passage 29 is provided in a middle portion of the groove 28 to communicate with the groove 28, and a lower flange bypass hole 30 is opened at one side of the lower flange passage 29 to communicate with the second outlet of the gas switching device 27.
In order to ensure sealing, the distance between the inner wall of the groove 28 and the outer wall of the lower slide 14 is greater than or equal to 0.5-1.2 mm, and the diameter d of the lower flange channel 29 is less than or equal to the width A of the groove 28.
When the central line of the groove 28 coincides with the central line of the lower slider 14 in the width direction, B-A is required to be more than or equal to 2 x (0.5-1.2) mm;
preferably, the single-side sealing distance of the groove 28 is between 0.5 and 1.2mm, i.e. B-A =2 × (0.5 and 1.2) mm.
When the lower rolling rotor 26 moves to the bottom dead center: the length C of the groove 28 is equal to or less than L + C and equal to or more than D +2e + (2-5) mm, namely the sum of the shortest distance from the end point of the groove close to the inner wall of the second cylinder and the length of the groove minus the sum of the length of the sliding piece and the stroke of the sliding piece is less than or equal to 2-5 mm;
wherein, A is the width of the groove 28, B is the width of the lower sliding piece 14, C is the length of the groove 28, D is the length of the lower sliding piece 14, and e is the eccentric amount of the crankshaft;
as another alternative, the groove 28 is disposed on the middle partition plate 12, and the lower flange channel 29 and the lower flange bypass hole 30 are also transferred to the middle partition plate 12, which is the same as that in embodiment 2 and will not be described again.
The sliding sheet, the flange or the middle partition plate is provided with a groove, the shape of the groove can be in various forms, a channel communicated with the groove is arranged on the finish machining end face of the flange or the middle partition plate, the channel is connected with a gas switching device, and the gas switching device is controlled through electromagnetic machinery to change the pressure in the groove into high pressure or low pressure, so that the working or locking of the sliding sheet is controlled, and the purpose of capacity control is achieved; the sliding sheet is pressed by the pressure generated by the pressure difference, so that the switching of the single-cylinder and double-cylinder operation can be reliably realized, and the stability and the reliability of the operation are higher; meanwhile, leakage can be well prevented by the regulation of the sealing size; when the sliding vane is static, the interior of the air cylinder and the tail part of the groove of the sliding vane are both high-pressure, so that air leakage of high pressure and low pressure is avoided; the structure is simple and reasonable, the volume is small, and the manufacturing cost is low.
The above-mentioned embodiments only represent some embodiments of the present invention, and the description thereof is specific and detailed, but not to be construed as limiting the scope of the present invention. It should be noted that, for those skilled in the art, without departing from the spirit of the present invention, several variations and modifications can be made, which are within the scope of the present invention. Therefore, the protection scope of the present invention should be subject to the appended claims.
Claims (10)
1. A variable capacity rotary compressor comprises a shell, a motor and a cylinder assembly, wherein the motor and the cylinder assembly are arranged in the shell and are connected through a crankshaft, and the variable capacity rotary compressor is characterized in that:
the air cylinder assembly comprises a first air cylinder, a second air cylinder, a first rolling rotor and a second rolling rotor which are respectively arranged in the first air cylinder and the second air cylinder and can eccentrically rotate, a first sliding sheet arranged in the first air cylinder, a second sliding sheet arranged in the second air cylinder, a middle partition plate, a first flange, a second flange and a gas switching device;
a groove is formed in the second sliding sheet or in the position, corresponding to the second sliding sheet, of the second flange or in the position, corresponding to the second sliding sheet, of the middle partition plate;
a gas channel is arranged between the groove and the gas switching device;
the gas switching device is used for switching the gas pressure at the groove between a high pressure and a low pressure, when the gas pressure at the groove is the high pressure, the second sliding sheet is in a working state, and when the gas pressure at the groove is the low pressure, the second sliding sheet is in a locking state.
2. A variable capacity rotary compressor according to claim 1, wherein:
the groove is arranged on the second sliding sheet and is positioned on the surface which is in contact with the second flange, and the gas channel is positioned on the second flange;
the distance from the inner wall of the groove to the outer wall of the second sliding sheet is greater than or equal to 0.5 mm-1.2 mm, and the diameter of the gas channel is smaller than or equal to the width of the groove.
3. A variable capacity rotary compressor according to claim 2, wherein:
when the second rolling rotor is positioned at the top dead center, the center of the gas channel is superposed with the center of the second sliding sheet, and the distance between the groove and the inner wall, closest to the outer edge of the second flange, of the groove and the outer edge of the second flange is 2-5 mm.
4. A variable capacity rotary compressor according to claim 1, wherein:
the groove is formed in the second flange and located on the surface, in contact with the second sliding piece, of the second flange, and the gas channel is located on the second flange.
5. A variable capacity rotary compressor according to claim 4, wherein:
and a bypass is further arranged on the side wall of the gas channel and is used for being communicated with the gas channel.
6. A variable capacity rotary compressor according to claim 4 or 5, wherein:
the distance from the inner wall of the groove to the outer wall of the second sliding sheet is greater than or equal to 0.5 mm-1.2 mm, and the diameter of the gas channel is smaller than or equal to the width of the groove.
7. A variable capacity rotary compressor according to claim 6, wherein:
when the second rolling rotor runs to the bottom dead center, the sum of the shortest distance from the end point of the groove close to the inner wall of the second cylinder and the length of the groove minus the sum of the length of the sliding piece and the stroke of the sliding piece is less than or equal to 2 mm-5 mm.
8. A variable capacity rotary compressor according to claim 1, wherein:
the groove is formed in the middle partition plate and located on the surface, in contact with the second sliding piece, of the middle partition plate, and the gas channel is located on the middle partition plate.
9. A variable capacity rotary compressor according to claim 8, wherein:
the distance from the inner wall of the groove to the outer wall of the second sliding sheet is greater than or equal to 0.5 mm-1.2 mm, and the diameter of the gas channel is smaller than or equal to the width of the groove;
when the second rolling rotor is positioned at the bottom dead center, the sum of the shortest distance from the end point of the groove close to the inner wall of the second cylinder and the length of the groove minus the sum of the length of the sliding piece and the stroke of the sliding piece is less than or equal to 2 mm-5 mm.
10. A variable capacity rotary compressor according to claim 1, wherein:
the gas switching device is at least one of a three-way valve and a four-way valve.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201220378264 CN202707496U (en) | 2012-07-30 | 2012-07-30 | Variable-capacity rotary compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201220378264 CN202707496U (en) | 2012-07-30 | 2012-07-30 | Variable-capacity rotary compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN202707496U true CN202707496U (en) | 2013-01-30 |
Family
ID=47587803
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 201220378264 Expired - Lifetime CN202707496U (en) | 2012-07-30 | 2012-07-30 | Variable-capacity rotary compressor |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN202707496U (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103573625A (en) * | 2012-07-30 | 2014-02-12 | 珠海格力节能环保制冷技术研究中心有限公司 | Volume variable rotation compressor |
| CN103821716A (en) * | 2014-03-03 | 2014-05-28 | 广东美芝制冷设备有限公司 | Two-stage rotary compressor and refrigeration circulating device with same |
| CN104654516A (en) * | 2013-11-21 | 2015-05-27 | 珠海格力电器股份有限公司 | Control method and system of variable-frequency variable-capacity compressor |
| CN104729138A (en) * | 2013-12-23 | 2015-06-24 | 珠海格力电器股份有限公司 | Air conditioner and capacity change judgment method thereof |
| US10254013B2 (en) | 2014-03-03 | 2019-04-09 | Guangdong Meizhi Compressor Co., Ltd. | Two-stage rotary compressor and refrigeration cycle device having same |
| CN110332115A (en) * | 2019-07-04 | 2019-10-15 | 珠海格力节能环保制冷技术研究中心有限公司 | Pump assembly, compressor and heat pump system |
-
2012
- 2012-07-30 CN CN 201220378264 patent/CN202707496U/en not_active Expired - Lifetime
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103573625A (en) * | 2012-07-30 | 2014-02-12 | 珠海格力节能环保制冷技术研究中心有限公司 | Volume variable rotation compressor |
| CN103573625B (en) * | 2012-07-30 | 2016-01-27 | 珠海格力节能环保制冷技术研究中心有限公司 | Rotary compressor with variable volume |
| CN104654516A (en) * | 2013-11-21 | 2015-05-27 | 珠海格力电器股份有限公司 | Control method and system of variable-frequency variable-capacity compressor |
| CN104654516B (en) * | 2013-11-21 | 2018-03-06 | 珠海格力电器股份有限公司 | Control method and system of variable-frequency variable-capacity compressor |
| CN104729138A (en) * | 2013-12-23 | 2015-06-24 | 珠海格力电器股份有限公司 | Air conditioner and capacity change judgment method thereof |
| CN104729138B (en) * | 2013-12-23 | 2017-08-01 | 珠海格力电器股份有限公司 | Air conditioner and capacity change judgment method thereof |
| CN103821716A (en) * | 2014-03-03 | 2014-05-28 | 广东美芝制冷设备有限公司 | Two-stage rotary compressor and refrigeration circulating device with same |
| US10254013B2 (en) | 2014-03-03 | 2019-04-09 | Guangdong Meizhi Compressor Co., Ltd. | Two-stage rotary compressor and refrigeration cycle device having same |
| CN110332115A (en) * | 2019-07-04 | 2019-10-15 | 珠海格力节能环保制冷技术研究中心有限公司 | Pump assembly, compressor and heat pump system |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN103573625B (en) | Rotary compressor with variable volume | |
| CN202707496U (en) | Variable-capacity rotary compressor | |
| EP3392507B1 (en) | Variable-capacity cylinder with sliding vane control structure and variable-capacity compressor | |
| EP3628871B1 (en) | Compressor, air conditioner, and method for assembling compressor | |
| CN103727034B (en) | Compressor | |
| KR101637446B1 (en) | Rotary compressor | |
| CN103557159B (en) | Rotary compressor | |
| KR102542439B1 (en) | Compressors and air conditioners | |
| CN109058106B (en) | Pump body assembly, compressor and dual-temperature air conditioning system | |
| CN203335407U (en) | Single-cylinder two-stage compression pump body and compressor | |
| CN108071590B (en) | Cylinder, compression mechanism and compressor | |
| JP2016513766A (en) | Rotary compressor, compressor for the same, air conditioner | |
| EP3244065B1 (en) | Variable displacement type compressor and refrigeration device having same | |
| CN109058107B (en) | Sealed rotary compressor and control method thereof | |
| KR101587174B1 (en) | Rotary compressor | |
| CN111075721B (en) | Pump body subassembly and variable volume compressor | |
| CN213838901U (en) | Rotary compressor and refrigeration cycle system | |
| CN212055114U (en) | Scroll compressor and air conditioner with same | |
| CN102124229B (en) | Rotary compressor | |
| CN103557157A (en) | Variable-capacity compressor and air-conditioning system | |
| CN210317754U (en) | Compressor variable volume structure, compressor and refrigeration cycle device | |
| US20110135526A1 (en) | Rotary compressor | |
| KR100621027B1 (en) | Modulation apparatus for rotary compressor | |
| CN202833168U (en) | Compressor | |
| CN101975165B (en) | Rolling piston refrigeration compressor capable of effectively utilizing space |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20130130 Effective date of abandoning: 20160127 |
|
| C25 | Abandonment of patent right or utility model to avoid double patenting |